Control for hydrodynamic machines



July 20, 1943. E; wlEDMANN CONTROL FOR HYDRODYNAMIC MACHINES Filed sept. 14, 19:58

` 2 sheets-sheet 1 uwI' I N V EN TGR.

ERNST .WEDMANN 62 BY 38 ATTORNEY..

July 20, 1943.y E. wll-:DMANN CONTROL FOR HYDRODYNAMIC MACHINES Filed Sept. 14.` 1958 2 Sheets-Sheet 2 l a/ L/a JNVENTOR. ERNST VV'IEDMANN BY. M

/ ATTORNEY- Patented July 20, 1943 CONTROL FOR HYDRODYAMIC MACHINES Ernst Wiedmann, Milwaukee, Wis., assigner to The Oilgear Company, Milwaukee, Wis., a cerporation of Wisconsin Application September 14, 1938, Serial No. 229,825 I zo eiaims. (ol. 121-41) This invention relates to controls for hydrodynamic machines ef the type which function as pumps when driven from a source of power and function as motors When supplied with motive` liquid.

The principal object7 of the invention is to provide a control by means of which the displacement ef a hydrodynamic machine maybe varied according to a predetermined schedule to thereby cause the volumetric delivery of said machine when functioning as a pump er'v the speed of said machine when functioning as a.

motor to vary according to such schedule.

Other and more specic objects and advantages Will appear from the description hereinafter given of apparatus in which the invention is embodied.

panying drawings in which the views are as follows:

Fig. 1 is a transverse vertical section through a pump te which the invention has been applied.

Fig. 2 is a View showing en a larger scale a part of the mechanism illustrated in Figf 1.

Fig. 3 is a developed top plan view of a part of a rotary valve forming a part of the invention, the View being taken in the plane of the line 3-3 of Fig. 2.

Figs. 4 and 5 are views similar to Fig. 3`but showing the valve rotated to positions difierent from that shown in Fig. 3.

Fig. 6 is a circuit diagram showing the invention applied to a pump which is employed to energize the motors of a hydraulically operated breaching machine.

Fig. 7 is a View showing one of the motors of the breaching machine With its piston in a position different from that shown in Fig. 6.

Figs. 8 and 9 are'views showing a control valve in positions different vfrom that shown in Fig. 6.

For the purpose of illustration, the invention has been shown as being applied te a pump I and the pump has been shown in Fig. 6 as being employed to drive a breaching machine having Work and tool carriages which must be operated in a predetermined sequence. Since the breaching machine is fully illustrated and described in Pateni; No. 2,190,642, it has been represented by a schematic showing of its hydraulic circuit.

It is deemed sufcient to state herein that the machine has a work slide 2 for advancing and retracting a piece of Work into and out of the path of a breaching tool carried by a tool slide 3 which is reciprocated vertically by a piston 4 arranged in a stationary cylinder 5, and a werk slide 2a for advancing and retracting another piece of werk into and out of the path. of a breaching tool carried by a tool slide 3a which is recipreeated vertically by a piston Iia arranged in a stationary cylinder 5a.

Work slides 2 and 2a are both reciprocated by aY hydraulic meter consisting of a cylinder 6 and a piston 'I whichis` fitted in cylinder 6 and functions both as almoter piston and as a valve.` .A rack 8 is connected to piston "1 and in meshwith a pinion 9 fixedupen a shaft i0 Whichis re-tat.;` able upon a stationary axis and has two levers or arms II and IIa fixed thereon. Arms Iiand` I Ia are spaced `degrees apart andconnected, respectively, to Work slides 2 and 2Et by links I2 and I2a.

The arrangement is such that, when piston 1 is moved toward the right, rack 8 will rotate pinion 9 and shaft I0 in a clockwise direction and cause arms II and IIa andlinks I2 and I2?L to advance slide 2 and retract slide 2a and, when piston I is moved toward the leit, rack 8 will rotate pinion 9 and shaft i6 in a countercleckwise direction and cause arms I i and IIa and links I 2 and Il!a to advance slide 2a and retract slide 2,. y

The parts are so proportioned that the stroke of motor 6-1 is just enough te rotate shaft I0 through substantially 180 and, when piston 'I is at either end of its strokes the axis of shaft I0 and the pivot peints of links I2 and I2a are in a straight line parallel to the path ei slides 2 and 2a so that the thrust of the tool against the Werk on either slide will impart substantially no turnthe other of two channels I5 and I6 Which are connected te cylinder 6 at er near the extreme ends thereof. i

Channels I5 and I6 are adapted to communicate, respectively, with two channels l'I and I8 which have the adjacent ends thereof spaced from each other and connected to cylinder 6 intermediate the ends thereof. The arrangement is such that, when piston I is in the position shown in Fig. 6, channel I'I is blocked and channel I8 is open to channel 6 and, when piston 'l is shifted to the position shown in Fig. '7, channel I8 will be blocked and channel il will be open to channel I5.

The other ends of channels II and I8 are connected, respectively, to the upper ends of cylinders 5 and 5a. Channel I'I is also connected through a channel I9 and a check valve 20 to channel I5 intermediate the ends thereof and through a check Valve 2I and a channel 22 to cylinder 5 at a point which is just below piston 4 when piston 4 is in its uppermost position. Check valves 20 and 2l permit liquid to ilow from cylinder 5 through channels 22, I'I and I9 into channel I5 but prevent it from flowing in the opposite direction.

Channel I8 is likewise connected lthrough a channel 23 and a check valve 24 to channel I6 intermediate the ends thereof and through a check valve 25 and a channel 26 to cylinder 5a at a point which is just below piston 4L when piston 4a is in its uppermost position. Check valves 24 and 25 permit liquid to ow from cylinder 5a through channels 25, I8 and 23 into channel I6 but prevent it from owing in the opposite direction.

Cylinders 5 and 5a have the lower ends thereof connected to each other by a channel 21 which is connected to a channel 28 through a manually operated shutoff valve 29 and choke 3D. Channel 28 is connected through a check valve 3l and a channel 32 to channel I5 and through a check valve 33 and a channel 34 to channel I5. Channel 2'I is also connected through a channel 35 to a relief valve 36 which discharges through a channel 31 into a reservoir 38 which is ordinarily formed in the casing of pump I and from which pump I is supplied with motive liquid.

The arrangement is such that, when `the parts are in the positions shown in Fig. 6 and pump I is caused to deliver liquid into channel I5, the liquid will enter the left end of cylinder 5 and move piston 'I toward the right, thereby causing slide 2 to be advanced and move the Work thereon into the path of a tool carried by slide 3 and causing slide 2a to be retracted and move the work thereon out of the path of a tool carried by slide 3B.

As soon as piston 'I moves a short distance, i-t blocks channel I8 and, when it reaches the end of its movement, it uncovers the end f channel II. Liquid from pump I may then flow through channel I5, cylinder B and channel I'I to the upper end of cylinder and move piston 4 downward on a working stroke, thereby moving tool slide 3 downward and causing the tool thereon to take a cut from the work on slide 2.

As piston 4 moves downward, it ejects liquid from the lower part of cylinder 5, and this liquid flows through channel 2'I to the lower end of cylinder 5a and raises piston 4a, thereby causing tool slide 3a to move upward simultaneously with the downward movement of tool slide 3. Piston 4a in moving upward will eject liquid from the upper part of cylinder 5a through channels IS and 23 and check valve 24 into channel I6 which at this time constitutes the return channel to pump I.

Since the displacement of cylinders 5 and 5a are the same, the liquid ejected from cylinder 5 tends to move piston 5a upward at practically the same rate as piston 4 moves downward but at the same time, liquid Will ilow from channel I5 through channel 32, check valve 3l, channel 28, choke 3U and channel 2l into lower end of cylinder 5a at a limited rate and cause piston 4a to rise at a rate slightly greater than the rate at which piston 4 descends. Consequently, piston 4a will reach the end of its up stroke before piston 4 reaches the end of its down stroke.

When piston lla reaches the end of its up stroke, it will uncover the end of channel 26 and then the liquid supplied to the lower end of cylinder 5a during continued downward movement of pist0n 4 flows through channel 2G, check valve 25, channels I8 and 23 and check valve 24 into channel I6.

When piston 4 reaches the end of its down stroke, a half cycle of operation has been completed and the machine comes to rest. The second half of the cycle may then be started by causing pump I to discharge into channel I6 which will cause the slides to move in the above described manner but in' directions opposite to those in which they move during the first half of the cycle.

Pump I should deliver liquid to cylinder 5 or 5a at a rate high enough to enable piston 4 or 4a to drive slide 3 or 3a at approximately the highest practical cutting speed of the tool carried thereby. However, cylinder 6 is much Smaller than cylinder 5 or 5a and, if pump I should deliver liquid thereto at the rate required to drive piston 4 or 4a at the desired speed, piston I would move slides 2 and 2a at such high speeds that the advancing slide would strike a damaging blow against the Stop which is always employed to accurately determine the broaching position of the work.

It is therefore desirable that the slides be moved at a rapid but regulated speed and, in order that the machine may operate smoothly, it is desirable that the slides be gradually accelerated. This is accomplished by means of a control which will cause the displacement of pump I to be varied according to a predetermined schedule.

Any suitable type of pump may be employed but, for the purpose of illustration, pump I has been shown as being of the .rolling piston type which is fully illustrated and described in Patent No. 2,074,068. It isdeemed suilcient to state herein that pump I has its pistons and cylinders arranged radially in a cylinder barrel 42 which rotates upon a stationary valve shaft or pintle 43 having formed therein ports and passages through which liquid flows to and from the cylinders, that the outer ends of the pistons react against an annular reaction surface 44 which in practice is formed in a separate rotatable thrust member carried by a slide block 45 but which has been shown as being formed in the slide block 45, that pump I will discharge liquid in a direction and at a rate depending upon the direction and the distance the axis of reaction surface 44 is oliset from the axis of cylinder barrel 42, and that slide block 45 is arranged in a casing 46 which permits it to be moved transversely of pintle 43 but prevents it from moving in any other direction.

Channels I5 and I6 are connected to pump I in communication with the passages formed in pintle 43. If cylinder barrel 42 is rotated in a `to chamber 60.

clockwise direction as viewed in Fig. 1, pump I will discharge liquid into channel I and have liquid returned toit through channel I6 when slide block 45 is shifted toward the right from its central position, and it will discharge liquid into channel I 6 and have liquid returned toit through channel l5 when slide block 45 is shifted toward the left from its central position. When slide block 45 is in its central or neutral position at which time reaction surface 44 is concentric with cylinder barrel 42, pump I is at zero stroke and no liquid will be delivered thereby.

In order to compensate for leakage losses and for the difference in the volume delivered by pump I and the volume returned thereto from an external circuit havingdifferential motors connected therein, means are provided to permit liquid returned to the pump in excess of pump requirements to be discharged into reservoir 38 and, when the volume returned to the pump is `less than pump requirements, to either permit the pump to draw the additional liquid required from reservoir 38 or to be supplied therefrom by a gear pump 50 which has been shown as a separate pump but which is ordinarily driven in unison with the main pump and arranged in the casing thereof according to the common practice.

As shown, communication between pump I and reservoir 38 is controlled by an automatic valve 5I having two spaced apart heads or pistons 52 and 53 arranged thereon and closely iitted in a bore 54 formed in a valve casing '55 which is arranged below slide block 45 and has a part thereof extending into the liquid in reservoir 38.

Piston heads 52 and 53 on valve 5I control communication between bore 54 and two channels 56 and 51 which connect channels i5 and I6 with bore 54 at two points spaced from oppo site ends thereof. The extremeV left lend of bore 54 is connected by a channel 58 to channel '56 intermediate the ends thereof and the extreme right end of bore 54 is connected by a channel 59 to channel 51 intermediate the ends thereof.

That part of bore 54 `between channels 56 and 51 communicates with a chamber 6I! formed in the lower part of valve casing 55 and communieating with reservoir 38 through a check valve 6I which permits pump `I to draw liquid freely from reservoir 38 but prevents liquid from being i expelled from chamber 60 except through a low pressure relief valve 62 having its inlet connected Gear pump 5|! draws liquid from reservoir 38 and discharges it into a low pressure supply channel 63 having three branches 63a, 631u and 63C. A part of the liquid discharged by gear pump 56. is used for control purposes, as will presently appear, and the remainder is exhausted through a relief valve 64 which has its inlet connected to' channel 631L and its `outlet connected to chamber 60 by channel 65.

The liquid discharged by gear pump 5i) into chamber iiin excess of the volume required to supercharge pump I is exhausted through relief valve'62 soA that, except when pump I is drawing liquid from reservoir 38 through check valve 3i, gear pump 56 is enabled to maintain in chamber 66 a pressure equal to the resistance of relief valve 62 and to maintain in channel 63 and` its branches a pressure equal to the sum of 'the re--' sistances of relief valves 62 and 64.

The arrangement is such that, when pump I starts to deliver liquid into channel l5, pressure extends from channel I6 through channels` 51 and 59 to the right end of bore` 54 and shifts valve 5I toward the left so that channel 51` is blocked by piston 53 and channel 56 is opened to chamber through bore 54 and, when pump I starts to deliver liquid into channel I5, pressure extends from channel I5 through channels 56 and 58 to the left end of bore 54 and shifts valve 5I toward the right to the position shown so that channel 56 is blocked by piston 52 and channel 51 is opened to chamber 60 through bore 54.

Valve 5I thus operates to automati-cally block the pressure side of the pump from chamberl) and to open the return side of the pump to chamber in either direction of pump delivery so that pump I can at no time discharge freely into reservo-irV 38, liquid returned to the pump in excess Vof pump requirements can at all times `be discharged through channel 56 or 51, bore 54, chamber 66 and relief valve 62 into reservoir 38, and any deciency in the liquid returned to the pump from an external circuit can be made up by liquid drawn by pump I through check valve 6i.

. Pump I is caused to deliver liquid in one direction or the other by shifting slide block 45 in one direction or the other from a central or neutral position.` This is accomplished by hydraulically actuated means operated by liquid supplied thereto from gear pump 50 under the control of a Valve which controls the rate, direction and extent of movement of slide block 45.

As sho-wn in Fig. l, slide block 45 is constantly urged toward the left by a hydraulic servo-motor consisting of a cylinder 16, which is formed ntegral with or connected to pump casing 46, and a piston 1i which abuts or is connected to the right side of slide block 45 and ttedin cylinder 10. Branch channel 63a is connected to cylinder 16 so that piston 1I is subjected at allV times to gear pump pressure. i l i Slide block 45 is adapted to be moved toward the right by a hydraulic servo-motor consisting of apiston 12, which has a larger effective pressure area than piston 1I and abuts or is con# nectedj to the left side or slide block 45, and a cylinder 13 which is formed integral with or con-` nected to pump casing 46 and has piston 12 tted therein. f

Cylinder 13 is closed at its outer end by a housing 'ifi having a bore 15 (Fig. 2) formed therein in axial alignment with an axial bore 16 which extends through piston 12 and through an extension or hub 11 formed upon the outer face of piston 12. The inner end of bore 16 communicates at all times with the interior of pump` casing 46 as by means of one or moreradial passages 13 formed in the inner end of piston 12.

Servomotor 12--13 is controlled by a rotary valve 8l which is iitted in bores 15 and 16 and provided upon its outer end with a pinion B2 for rotating it and for restraining it from axial movement.

Valve BHI is provided with an internal pase sage 83 having one end thereof in communication at all times with anannular groove 84 which is formed in the wall of bore 15 and has branch channel 631 connected thereto so that groove 84 and passage 83 are constantly supplied with mo tive Vliquid-from gear pump 50. f

TheV other end of passage 83 opens into a groove 85 which is formed in the peripheral surface of valve 8l adjacent a `port 86 formed in hub 11. Port 86 is adapted, uponrotation of valve 8| in one direction or the other, to provide communication between the interior of cylinder 13 and either groove 85 or a groove 81 which is formed in the peripheral surface of valve 8| and opens into the inner end of bore 16.

The arrangement is such that, when port 85 registers with groove 85, liquid from gear pump I] will ow through channels 63 and 63h, groove 84, passage 83, groove 85 and port 86 into cylinder 13 and act upon piston 12. Since the effective pressure area of piston 12 is greater than that of piston 1 I, the liquid entering cylinder 13 will cause piston 12 to move slide block 15 toward the right and piston 1I will expel liquid from cylinder 18 through relief valves 64 and 62. When port 86 registers with groove 81, cylinder 13 is open to drain and the liquid constantly supplied to cylinder 18 will cause piston 1I to move slide block 45 toward the left and cause piston 12 to expel liquid from cylinder 13 through port 86, groove 81, the inner end of bore 16 and passage 18 into pump casing 45.

Port 88 and grooves 85 and 81 are so proportioned that, when 8| is stationary, opposite edges or corners of port 88 aline with adjacent edges of grooves 85 and 81 so that the slightest relative movement between port 86 and grooves 85 and 81 axially of the valve 8| will open communication between port 88 and one or the other of grooves 85 and 81.

Consequently, when valve 8| is stationary, any movement of slide block 45 toward the left will open port 88 to groove 85 and permit liquid to enter cylinder 13 and cause piston 12 to return slide block 45 to its correct position, and any movement of slide block 45 toward the right will open port 86 to groove 81 and permit liquid to escape from cylinder 13 and permit piston 1I to return slide block 45 to its correct position.

Communication between port 86 and one or the other of grooves 85 and 81 may be established by rotating valve 8l in one direction or the other to thereby cause slide block 45 to be moved in one direction or the other. Since porI'l 86 is formed in hub 11 so that it moves with piston 12 and slide block 45, valve 8| and hub 11 constitute a follow-up Valve mechanism which permits liquid to iiow to and from cylinder 13 only while valve 8| is rotating. Consequently, movement of slide block 45 ceases at substantially the same instant that valve 8| ceases to rotate.

If grooves 85 and 81 were spiral, slide block 45 would be moved through a distance proportional to the angular distance through which valve 8| was rotated, and it would be moved at a rate determined by the pitch of grooves 85 and 81 and by the rate at which valve 8| was rotated. Therefore, if grooves 85 and 81 were spiral and valve 8| were rotated at a uniform rate, the volumetric delivery of pump I would be uniformly varied if the hydrodynamic machine were functioning as a pump or the motor speed would be uniformly varied if the hydrodynamic machine were functioning as a motor.

In the illustration, it is desired to operate motor I--1 at a predetermined speed until it has completed its stroke and to then operate motors 4-5 and lla-5a at a predetermined speed. This is accomplished by so forming grooves 85 and 81 that the contours of their adjacent edges correspond to the functions desired. Since the pump chosen for illustration is reversible, grooves 85 and 81 extend around valve 8| in both directions from a line extending axially through port 83 which line may be considered as the centerline of the valve.

In the illustration given, each hydraulic motor should be operated at the same speed in both directions so that the volumetric delivery of pump should be varied in both directions according to the same schedule. Consequently, grooves 85 and 81 are shown as being substantially the same but opposite hand to each other with the exception that the inner or right hand end of groove 81 is open to the inner end of bore 16 while the corresponding end of groove 85 is closed.

Since with the above exception grooves 85 and 86 are substantially opposite hand to each other, a description of one will suice for both. Consequently, each edge portion of each groove has been indicated by a reference character consisting of the reference numeral of the groove with an exponent added thereto and corresponding portions of the two grooves indicated by corre-y sponding exponents.

As shown in Figs. 3 to 5, the edge of groove 85 adjacent groove 81 has a straight portion 85a which extends circumferentially in both directions from the centerline of valve 8|. One end of edge portion 85a joins one end of a spiral portion 85b the other end of which joins one end of the far edge 85c of groove 85.

The other end of straight portion 85a joins one end of a short spiral portion 85d the other end of which joins one end of a short straight or circumferential portion 85e. The other end of straight portion 85e joins one end of a short spiral portion 85f the other end of which joins one end of a longer circumferential portion 85g. The other end of circumferential portion 85g joins a spiral portion 85h the other end of which is joined to the other end of far edge 85c by an edge portion 85k.

As explained above, groove 81 is substantially opposite hand to 85 except that its inner end is open to the inner end of bore 15. Instead of edge portions 81D and 81c being joined to each other as is the case with the corresponding edge portions of groove 85, they extend to the end of valve 8| to thereby open the inner end of groove 81 to the inner end of bore 16.

Vhen valve 8| is in its central or neutral position as shown in Fig. 3, edge portions 85e and 81e are in alinement with Opposite edges of port 86 and slide block 45 is in its neutral position so that no liquid will be delivered by pump I. When valve 8| is rotated in one direction or the other, an edge portion of one or the other of grooves 85 and 81 will overlap one or the other edges or corners of port 86 to permit liquid to flow to or from cylinder 13 and thereby cause slide block 45 to be shifted in one direction or the other.

Valve 8| is rotated by means of the pinion 82 fixed thereto. As shown, pinion 82 meshes with a rack 88 formed on a piston or plunger 89 which is closely fitted in a bore 98 formed in the outer part of housing 14, Bore 98 communicates at the opposite end thereof with two pressure chambers 9|r and SIL (Fig' 6) which are also formed in housing 14.

Plunger 89 is the same length as bore 90 and is urged towards its central or neutral position by two springs 82R and SZL arranged, respectively, in pressure chambers SIR and SIL with the outer ends thereof in engagement with the outer ends of the chambers and the inner ends thereof in engagement, respectivly, with two spring retainers 93R and 93L which engage opposite ends of plunger 89.

Spring retainers 93R and 9311 are supported, respectively, upon two small diameter stops 94R and 941- which are fixed to or formed upon opposite ends of plunger 89 and extend through the spring retainers to limit the movement of,

plunger 89 in each direction.

When liquid under pressure enters one or the other of chambers SIR and 9|L, it will act upon an end of plunger 89 and shift it in one direction or the other and thereby cause rack 88 and pinion 82 to rotate valve 8| in one direction or the other. When the chamber to which pressure liquid has been supplied is opened to drain, the spring in the opposite chamber will move plunger 89 to its central position and thereby cause rack 88 and pinion 82 to rotate valve 8| to its neutral position.

Plunger 89 is adapted to be shifted in one direction or the other by liquid supplied by gear pump 50 to one or the other of pressure chambers SIR and SIL. The rate at which plunger 89 is shifted is controlled by an adjustable choke 95 (Fig. 6) and the direction in which plunger 89 is shifted is controlled by a valve 96 fitted in bore 91 of a valve casing 98.

Choke 95 has its inlet connected to branch 63c of gear pump supply channel 63 and its outlet connected b-y a channel 99 to an annular groove or port which is formed in the Wall of bore 91 betweentwo similarly formed annular grooves or ports |0| and |02 which are spaced therefrom and from the ends of bore 91 and connected, respectively, by channels |03 and |04 to pressure chambers SIR and 9|L so that liquid from gear pump 50 may flow at a limited rate to one or the other of chambers 9|R and 9|L depending upon the position of valve 96.

In order that liquid may escape from the pressure chambers, both ends of bore 91 are connected to a drain channel |05 which discharges into reservoir 38, and valve 96 controls communication betweeneach of ports |0| and |02 and the adjacent end of bore 91.

l Valve 96 may be shifted in any desired manner but ordinarily a control element is manually operated to cause valve 96 to be shifted from the neutral position shown in Fig. 6 to the position shown in Fig. 8 or to the position shown in Fig. 9to thereby initiate a cycle of operation, and it is ordinarily returned to its neutral position automatically at the end of the cycle such as when tool slides 3 and 3a reach the ends of their strokes.

Operation When valve 96 is in its central or neutral position as shown in Figy, pressure cham-bers 94R and 941' are open to drain and plunger 89 is held in its central or neutral position 'by springs 92R and 92L. When plunger 89 is in its neutral position, Valve 8| is in its neutral position with edge portions 85'3 and 81e of grooves 85 and 81 in alinement with opposite edges of port 86, as shown in Fig. 3, and slide block 45 will be in its central or neutral position as shown in Fig. 1 so that pump will be at zero stroke and no liquid will be discharged thereby.

When valve 96 is shifted toward the right to the position shown in Fig. 8, liquid from gear pump 59 (Fig. l.) may flow through channel 63, branch E30, choke 95 (Fig. 6), channel 99, bore 91 and channel lil@ to pressure chamber SIL and cause plunger 89 to move toward the right and expel liquid from chamber 9|R through channel (|03 and bore 91 into drain channel |05. Choke 95 will restrict the ilow of liquid and thereby cause plunger 89 to move at a very slow uniform rate.

Movement of plunger 89 toward the right causes rack 88 to rotate pinion 82 and valve 8| in a counterclockwise direction in respect to Fig. 6, thereby causing the adjacent edges of grooves and 81 to move along the opposite edges of port 86.

During rotation of Valve 8| through the first few degrees, straight portions 85e and 81e will remain in alinement with the edges of port 86 and slide block 45 will remain stationary but, as soon as spiral edge portion 85f overlaps the corner of port 86 as shown in Fig. 4, gear pump liquid will enter cylinder 13 (Fig. 2) and cause piston 'l2 to move slide block 45 toward the right, thereby causing pump to deliver liquid through channel I5 (Fig. 6) to the left end of cylinder 6.

During the time that edge portion 85f overlaps the corner of port 86, gear pump liquid will continue to loW into cylinder 13 and cause piston 'i2 to move slide block 45 toward the right at a rate dependent upon the speed of plunger 89 and the pitch of edge portion 85f.

When the end of edge portion 85f passes the corner of port 86, circumferential edge portion 85g will aline with one edge of port 86 andcircumferential edge portion 81a will aline with the other edge of port 86 so that no liquid can ow to or escape 'from cylinder 13. Then during continued rotation of valve 8|, slide block 45 will remain stationary and pump will deliver liquid through channel |5 to cylinder 6 at a desired rate which is proportional to the distance edge portion 85g is spaced from edge portion 85e axially of valve 8|. i

The volumetric delivery of pump is thus gradually increased from zero to a desired rate so that the liquid delivered by pump through channel |5 to the left end of cylinder 6 will move piston 1 toward the right and gradually accelerate it from a stationary position to a desired speed and then move it at thatspeed to the end of its stroke.

Choke is ordinarily adjusted to so regulate thespeed oi plunger 89 that the end of circum-` ferential edge portion 95g Will pass the corner of port 86 and spiral edge portion 85h will start to overlap the corner of port 86 at approximately the same time that piston 1 reaches the end of its stroke and uncovers the end of channel |1 so that the liquid discharged by pump will flow therethrough to the upper end of cylinder 5 and move piston 4 downward.

As soon as spiral edge portion 85h overlaps the corner of port 86, gear pump liquid will enter cylinder 13 and cause piston 12 to move slide block 45 farther toward the right at a rate dependent upon the speed of plunger 89 and the pitch of edge portion 85h, thereby causing the volumetric delivery of pump-I to be gradually increased with the result that piston 4 is gradually accelerated.

Plunger 89 will continue to rotate valve 8| and thereby cause the displacement of pump I and the speed of piston 4 to be gradually increased until further movement of plunger 89 is arrested by stop 94R at which time port 86 will move out of communication with groove 85 so that slide block 45 will become stationary and pump will continue to discharge liquid at a predetermined rate to thereby cause piston 4 to move at a desired speed as long as valve 8| remainsstationary.

The liquid expelled from the lower end of cylindcr by piston fl during its downward movement flows through channel 2l to the lower end of cylinder E and causes piston ia to raise slide 3a as previously explained.

When piston 4 reaches the end of its down stroke, valve 9S is automatically shifted in any suitable manner from the position shown in Fig. 8 to the position shown in Fig. 6 in which position of valve SS channel Idd is open to drain channel |05 so that spring 92B will quickly shift plunger 89 to its neutral position and thereby cause rack 88 and pinion 82 to rotate valve 8i clockwise to its neutral position.

As soon as valve 8l starts to rotate in a clockwise direction, edge portion Bib overlaps the corner of port 86 so that liquid can escape from cylinder 'I3 and piston ll can move slide block 45 toward the left to reduce the displacement of pump I.

During continued rotation of valve Gi, edge portions 87h, ala and Bld will successively overlap a corner or edge of port 85 and slide block 65 will continue to move rapidly toward the left until valve 8| stops in a neutral position at which time edge portions 35e and 82'@ will be in alinement with opposite edges of port 85, as shown in Fig. 3, and slide block 45 will come to rest in its neutral or zero stroke position. The broaching machine has thenv completed a half cycle of operation.

The second half of a cycle of operation may be initiated by shifting valve Q toward the left to the position shown in Fig. 9. With valve 96 in that position, liquid from gear pump 50 may flow to channel 63, branch 63e, choke 95, channel 99 bore 97 and channel |63 to pressure chamber SIR and cause plunger 89 to move toward the left and expel liquid from chamber SIL through Channel IM and bore QI into drain channel |05. Choke 95 will restrict the flow of liquid and thereby cause plunger 89 to move at a very slow uniform rate.

Movement of plunger 89 toward the left causes rack 88 to rotate pinion 82 and valve 8| in a clockwise direction in respect to Fig. 6, therebyv causing the adjacent edges of grooves 85 and 8'! to move along the opposite edges of port 86.

During rotation of valve 8l through the first few degrees, straight portions 85e and 81 will remain in alinement with the edges of port 86 and slide block 45 will remain stationary but, as soon as spiral edge portion 8'If overlaps the corner of port 85, liquid can escape from cylinder I3 and piston 'II will move slide block 45 toward the left and thereby cause pump I to deliver liquid through channel I6 to the right end of cylinder 6.

During continued rotation of valve 8l, spiral edge portion Blf will at first overlap the corner of port 86 so that slide block 45 will continue to move toward the left through a predetermined distance, then straight edge portion 81g will aline with the edge of port 86 so that slide block -45 will remain stationary for a predetermined interval of time, and then edge portion 87h will overlap the corner of port 8B as shown in Fig. 5 so that slide block 45 will be moved farther toward the left to a predetermined point.

The volumetric delivery of pump I is thus gradually increased from zero to a predetermined amount, then maintained at that amount for a predetermined interval of time, then gradually increased to a predetermined maximum, and then maintained at that maximum until valve 8| is returned to its neutral position.

Consequently, the liquid discharged by pump I will enter the right end of cylinder 6 and gradually accelerate piston 1 from a stationary position to a predetermined speed, then move it at that speed to the end of its stroke, then ow through channel I8 to the upper end of cylinder 5a and move piston 4a downward at a speed which gradually increases from a slow speed to a high speed and then remains constant until piston la reaches the end of its down stroke at which time valve 96 automatically returns to its neutral position to cause pump displacement to be reduced to zero and the machine brought to rest as previously explained.

The apparatus described herein is susceptible of various modifications and adaptations without departing from the scope of the invention as hereinafter claimed. l

The invention is hereby claimed as follows:

1. A control, comprising a stationary cylinder, a piston tted in said cylinder, means for supplying motive liquid to said cylinder to move said piston, valve mechanism for controlling the flow of liquid to and from said cylinder, and means for operating said valve mechanism at a uniform rate, said valve mechanism having cooperating ports and passages so arranged as to vary the flow of liquid to and from said cylinder according to a predetermined schedule and thereby cause the movement of said piston to be varied according to said schedule during operation of said valve mechanism at said uniform rate.

2. A control, comprising a hydraulic motor for moving a member, means for supplying motive liquid to said motor to energize the same,

a follow-up valve mechanism for controlling the flow of liquid to and from said motor and having one part thereof movable with said member and another part thereof independently movable whereby liquid may flow to or from said motor only during movement of said independently movable valve part, and means for moving said independently movable valve part at a uniform rate, said valve parts having cooperating ports and passages so arranged as to vary the flow of liquid to and from said motor according to a predetermined schedule and thereby cause said member to be moved according to said schedule during movement of said independently movable valve part at said uniform rate.

3. A control, comprising a hydraulic motor for moving a member, means for supplying motive liquid to said motor to energize the same, a follow-up valve mechanism for controlling the flow of liquid to and from said motor and including two valve parts one of which is rotatable and the other of which is movable with said member axially of said rotatable part, and means for rotating said rotatablepart at a uniform rate, said valve parts being tted one within the other and having cooperating ports and passages so arranged as to vary the flow of liquid to and from said motor according to a predetermined schedule and thereby cause said member to be moved according to said schedule during rotation of said rotatable part at said uniform rate.

4. A control, comprising a hydraulic motor for moving a member, means for supplying motive liquid to said motor to energize the same, a follow-up valve mechanism for controlling the flow of liquid to and from said motor and having one part thereof movable with said member and another part thereof independently movable whereby liquid may flow to or from said motor only during movement of said independently movable valve part, hydraulic servo-motor means for moving said independently movable valve part at a uniform rate, and `means for supplying motive liquid to said servo-motor means including a choke for restricting the flow of liquid thereto to thereby regulate the speed thereof and a reversing valve for controlling the operation of said servo-motor means, said valve parts having cooperating ports and passages so arranged as to vary the flow of liquid to and from said motor according to a predetermined schedule and thereby cause said member toy be moved according to said schedule during movement of said independently movable valve part at said uniform rate.

5. A control, comprising a hydraulic motor for moving a member, means for supplying motive liquid to said motor to energize the same, a follow-up valve mechanism for controlling the now of liquid to and from said motor and including tn wo valve parts one of which is rotatable and the other of which is movable with said member axially of said rotatable part, hydraulic servo-motor means for rotating said rotatable part at a uniform rate, and means for supplying motive liquid to said servo-motor` means including a choke for restricting the flow of liquid thereto to thereby regulate the speed thereof and a reversing valve for controlling the operation of said servo-motor means, said valve parts being fitted one within the other and having cooperating ports and passages so arranged as to vary the flow of liquid to and from said motor according to a predetermined schedule and thereby .cause said member to be moved according to said schedule during rotation of said rotatable part at said uniform rate.

6. A control, comprising a hydraulic motor for moving a member, a source of pressure liquid, means for supplying liquid from said source to said motor to energize the same, and means for controlling the flow -of liquid to and from said motor including a valve cylinder movable with said member, a rotary valve fitted in said cylinder and forming therewith a follow-up valve mechanism, said cylinder and valve having cooperating ports and passages so arranged that liquid may now through said valve mechanism during rotation of said valve through a certain part of its range and be prevented from Iiowing therethro-ugh during rotation of said valve through a different part of its range, and means for rotating said valve.

7. A control, comprising a hydraulic motor for moving a member, a source of pressure liquid, means for supplying liquid from said source to said motor to energize the same, and means for controlling the now of liquid to and from said motor `including a Valve cylinder movable with said member, a rotary valve fitted in said cylinder and forming therewith a follow-up valve mechanism, said cylinder and valve having coop erating ports and passages so arranged that liquid may flow through said valve mechanism during rotation of said valve through a certain part of its range and be prevented from flowing therethrough during rotation of said valve through a diiferent part of its range, means including a hydraulic servo -motor for rotating said valve, means for supplying motive liquid to said servo-motor, a valve for controlling said servo-motor, and means for regulating the flow of liquid to said servo-motor to thereby regulate the speed of said rotary valve.

Y 8. A control, comprising a hydraulic motor for moving la member, a source of pressure liquid,

means for supplying liquid from said source to said motor to energize the same, and means for controlling the flow of liquid to and from said motor including a Valve cylinder movable with said member, a rotary valve fitted in said cylinder and forming therewith a follow-up` valve mechanism, said cylinder and valve having cooperating ports and passages so arranged that liquid may flow through said valve mechanism during rotation of said valve through a certain part of its range and'be prevented from owing therethrough during rotationlof said valve through a different part of its range, means including a hydraulic servo-motor for rotating said valve, means for supplying motive liquid to said servomotor, means for regulating the ow of'liquid to said servo-motor to thereby regulate the rotary speed of said valve, a control valve operable either to direct said liquid to said servo-motor or to connect said servo-motor to drain to thereby either energize or deenergize said servo-motor, and spring means for .causing said valve rotating means to rotate said rotary valve `to a neutral position upon said servo-motor being deenergized.

9. A control, comprising a hydraulic motor for moving a member, a source of pressure liquid, means for supplying liquid from said source to said motor to energize the same, and means for controlling the ilow of liquid to and from said motor including a valve cylinder movable with said member and having a port through which liquid may flow to and from said motor, a rotary valve iitted in said cylinder and having formed in its peripheral surface two spaced apart grooves one of which is connected to said yor the other causes one or the other of said grooves to communicate with said port to permit liquid to flow to or from said motor` and thereby cause said motor to shift said member in one direction or the other, a stationary cylinder,` a plunger fitted in said cylinder and provided with a rack, a pinion meshing With said rack and xed to said valve to rotate it during movement of saidplunger, spring means for retaining said plunger in a neutral position, means for supplying liquid to said cylinder to cause said plunger to move from its neutral position, means forreg ulating the flow of liquid to said cylinder` to thereby regulate the speed of said plunger, and a valve for either directing said liquid to said cylinder to cause said plunger to be moved ata regulated rate or for connecting said cylinder to drain to thereby permit said spring means to return said plunger at high speed to its neutral position.

l0. A control, comprising a hydraulic motor for moving a member, a source of pressure liquid, means for supplying liquid from said source to said motor to energize the same, and means for controlling the low of liquid to and from said motor including a valve cylinder movable with said member and having a port through which liquid may flow to and from said motor, a rotary valve fitted in said cylinder and having formed in its peripheral surface two spaced apart grooves one of which is connected to said source and the other of which is connected to drain whereby communication between saidv port and one or the other of said groovespermits liquid to ow to or from said motor and cause said motor to shift said member in one direction or the other, said grooves being arranged upon opposite sides of said port with the adjacent edges thereof normally in alinement with opposite edges of said port and each of the adjacent edges of said grooves consisting of alternate circumferential and spiral portions whereby a spiral edge porti-on of one or the other of said grooves will overlap the adjacent edge of said port and cause that groove to communicate with said port during one part of the rotary movement of said valve and circumferential' edge portions to aline with opposite edges of said port during another part of the rotary movement of said valve, and means for rotating said valve.

11. A control, comprising a hydraulic motor for moving a member, a source of pressure liquid, means for supplying liquid from said source to said motor to energize the same, and means for controlling the iiow of liquid to and from said motor including a valve cylinder movable with said member and having a port through which liquid may flo-W to and from said motor, a rotary valve tted in said cylinder and having formed in its peripheral surface two spaced apart grooves one of which is connected to said source and the other of which is connected to drain whereby communication between said port and one or the other of said grooves permits liquid to flow to or from said motor and cause said motor to shift said member in one direction or the other, said grooves being arranged upon opposite sides of said port with the adjacent edges thereof normally in alinement with opposite edges of said port and each of the adjacent edges of said grooves consisting of alternate circumferential and spiral po-rtions whereby a spiral edge portion of one or the other of said grooves will overlap the adjacent edge of said port and cause that groove to communicate with said port during one part of the rotary movement of said valve and circumferential edge portions to aline with opposite edges of said port during another part of the rotary movement of said valve, means for rotating said valve, and means for controlling said valve rotating means to thereby regulate the speed of said valve,

12. A control, comprising a hydraulic motor for moving a member, a source of pressure liquid, means for supplying liquid from said source to said motor to energize the same, and means for controlling the flow of liquid to and from said motor including a valve cylinder movable with said member and having a port through which liquid may flow to and from said motor, a rotary valve tted in said cylinder and having formed in its peripheral surface two spaced apart grooves one of which is connected to said source and the other of which is connected to drain whereby communication between said port and one or the other of said grooves permits liquid to flow to or from said motor and cause said motor to shift said member in one direction or the other, said grooves being arranged upon opposite sides of said port with the adjacent edges thereof normally in alinement with opposite edges of said port and each of the adjacent edges of said grooves consisting of alternate circumferential and spiral portions whereby a spiral edge portion of one or the other of said grooves will overlap the adjacent edge of said port and cause that groove to communicate with said port during one part of the rotary movement of said valve and circumferential edge portions to aline with opposite edges of said port during another part of the rotary movement of said valve, servomotor means for rotating said valve, means for energizing said servo-'motor means, and means for controlling the speed of said servo-motor means to thereby control the rate at which said member is shifted.

13. A control, comprising a hydraulic motor for moving a member, a source of pressure liquid, means for supplying liquid from said source to said motor to energize the same, and means for controlling the flow of liquid to and from said motor including a valve cylinder movable with said member and having a port through which liquid may flow to and from said motor, a rotary valve tted in said cylinder and having formed in its peripheral surface two spaced apart grooves one of which is connected to said source and the other of which is connected to drain whereby communication between said port and one or the other` of said grooves permits liquid to ow to or from said motor and cause said motor to shift said member in one direction or the other, said grooves being arranged upon opposite sides of said port with the adjacent edges thereof normally in alinement with opposite edges of said port and each of the adjacent edges of said grooves consisting of alternate circumferential and spiral portions whereby a spiral edge portion of one or the other of said grooves will overlap the adjacent edge of said port and cause that groove to communicate with said port during one part of the rotary movement of said valve and circumferential edge portions to aline with opposite edges of said port during another part of the rotary movement of said valve, means including a hydraulic servo-motor for rotating said valve, means for supplying motive liquid to said servomotor, a valve i'or controlling said servo-motor, and means for regulating the flow of liquid to said servo-motor to thereby regulate the speed of said rotary Valve.

14. A control, comprising a hydraulic motor for moving a member, a source of pressure liquid, means for supplying liquid from said source to said motor to energize the same, and means for controlling the flow of liquid to and from said motor including a valve cylinder movable with said member and having a port through which liquid may flow to and from said motor, a rotary valv-e fitted in said cylinder and having formed in its peripheral surface two spaced apart grooves one oi which is connected to said source and the other of which is connected to drain whereby communication between said port and one or the other of said grooves permits liquid to flow to or from said motor and cause said motor to shift said member in one direction or the other, said grooves being arranged upon opposite sides of said port with the adjacent edges thereof normally in alinement with opposite edges of said port and each of the adjacent edges of said grooves consisting of alternate circumferential and spiral portions whereby a spiral edge portion of one or the other of said grooves will overlap the adjacent edge of said port and cause that groove to communicate with said port during one part of the rotary movement of said valve and circumferential edge portions to aline with opposite edges of said port during another part of the rotary movement or said valve, means including a hydraulic servo-motor for rotating said valve, means for supplying motive liquid to said servomotor, means for regulating the iiow of liquid to said servo-motor to thereby regulate the rotary speed of l said valve, a controlr valve operable either to direct said liquid to said servo-motor or to connect said servo-motor to drain to thereby either energizeor deenergize saidiservo-motor, and spring means for causing said valve rotating means to rotate said rotary valve toa neutral position upon said servo-motor being deenergized. i l l 15. A control, comprising a hydraulic motor for moving a member, a source of pressure liquid, means for supplying liquid from said source to said motor to energize the same, 'and means for controlling the flow of liquid to and fromsaid motor including a valve cylinder movable with said member and having port through which 1i-A quid may flow to and from said motor, a rotary valve tted in said cylinder and having formed in its peripheral surface two spaced apart grooves one of which is connected to said source and the other of which is connected to drain whereby communication between said port and one or the other of said grooves permits liquid to flowto or from said motor and cause said motor to shift said member in one direction or the other, said grooves being arranged upon opposite sides of said port with the adjacent edges thereof normally in alinement with opposite edges of said port and each of the adjacent edges of said grooves consisting of lalternate circumferential and spiral portions whereby a spiral edge portion of one or the other of said grooves will overlap the adjacent edge of said port and cause that groove to communicate with said port during one part of the rotary movement of said valve and circumferential edge portions to aline with opposite edges of said port during another part of the rotary movement of said valve, a stationary cylinder, a plunger fitted in said cylinder and provided with la rack, a pinion meshing with said rack and fixed to said valve to rotate it during movement of said plunger, spring means for retaining said plunger in a neutral position, means for supplying liquid to said cylinder to cause said plunger to move from its neutral position, means i for regulating the flow of liquid to said cylinder to thereby regulate the speed of said plunger, and a valve for either directing said liquid to said cylinder to cause said plunger to be moved at a regulated rate or for connecting said cylinder to drain to thereby permit said spring means to return said plunger at high speed to its neutral position.

16. The combination, with a stationary cylinder, a piston fitted in said cylinder and constantly urged in one direction, means for supplying to said cylinder motive liquid for moving said piston in. the opposite direction, a valve casing carried by said piston, a rotary valve fitted in said casing and in the end portion of said cylinder for controlling the flow of liquid to and from said y cylinder to thereby control the movement of said ingtdsaid cylinder motive liquid for movingsaid piston-*in the opposite direction, a valve casing carriedbysaidipiston, a rotary valve fitted in said casingand in the end portion of said cylinder for controlling the flow of liquid to and from said cylinder Ato thereby control the movement of said piston, and` rnea'ri's for rotating said valve in one direction-or Atheother ata uniform rate,` said `valve and 'said-casing having cooperating ports and passages so arranged as to'cause an intermittent'flow of vliquid to' or from said cylinder during rotation of said valve at said uniform rate to thereby cause said piston to be moved intermittently.

18. The combination, with `a stationary cylinder, a piston fitted in said cylinder and constantly urged in one direction, means for supplying to said cylinder motive liquid for moving said piston in the opposite direction, a valve casing carried by said piston, a rotary valve fitted in said casing land in the end portion of said cylinder for controlling the flow of liquid to and from said cylinder to thereby control the movement of said piston, a gear fixed upon said valve, a rack meshing with said gear, hydraulic servo-motor means for reciprocating said rack to thereby rotate said valve, and means for supplying vpressure liquid at a uniform rate to one end or the other of said servo-motor means to energize the same and thereby cause said servo-motor means to rotate said valve in one direction or the other at a uniform rate, said valve and said casing having cooperating ports and passages so arranged as to cause an intermittent flow of liquid to or from said cylinder during rotation of said valve at said uniform rate to thereby cause said piston-to be moved intermittently.

19, The combination, with a stationary cylinder, a piston fitted in said cylinder and constantly urged in one direction and adapted to be moved in the opposite direction by liquid supplied to said cylinder, a valve casing carried by said piston and having a port for directing liquid to and fromsaid cylinder, a rotary valve fitted in said casing and in the end portion of said cylinder and provided with a passage, means for supplying motive liquid to said passage, said valve having formed in the peripheral surface thereof upon opposite sides of said port two lgrooves one of which. communicates with said passage and the other of which is connected to a drain, the adjacent edges of said grooves being normally in alinement with opposite edges of said port 'and each consisting of alternate spiral and circumferential portions so arranged that rotation of said valve' at a uniform rate in one direction or the other will permit liquid to flow to or from said cylinder according to a predetermined schedule and cause said piston to be moved in one direction or the other according to said schedule, and means for rotating said valve in one direction or the other at a uniform rate.

20. The combination, with a stationary cyl- Kinder, a piston fitted in said cylinder and constantly urged in one direction and adapted to be termined schedule-and cause said piston' to be 10A moved in one direction or the other according to said schedule, a gear xed upon said valve, a rack meshing with said gear, hydraulic servomotor means for reciprocating said rack to thereby rotate said valve, and means for supplying pressure liquid at a uniform rate to one end or the other of said servo-motor means to energize the same and thereby cause said servo-motor means to rotate said valve in one direction or the other at a uniform rate.

ERNST WIEDMANN. 

